Control apparatus for multi-valves and the like



March 28, 1961 J. A. MISCOVICH CONTROL APPARATUS FOR MULTI-VALVES ANDTHE LIKE Filed Nov. 4, 1957 3 Sheets-Sheet 1 INVENTOR JOHN A. MISCOVICHBY W ATTORNEY March 1951 J. A. MISCOVICH 2,976,742

CONTROL APPARATUS FOR MULTI-VALVES AND THE LIKE Filed Nov. 4, 1957 3Sheets-Sheet 2 T'IE E' Is I2.

INVENTOR JOHN A. MISCOVICH ATTORNEY March 28, 1961 J. A. MISCOVICHCONTROL APPARATUS FOR MULTI-VALVES AND THE LIKE 3 Sheets-Sheet 3 F'IE EIINVENTOR JOHN A. MISOOVICH BY wag/ aw.

ATTORNEY CONTROL APPARATUS FOR MULTI-VALVES AND THE LIKE John A.Miscovich, Fairbanks, Alaska, assignor, by mesne assignments, to John A.Miscovich, Los Angeles, Calif., and Paul E. Fiilio and J. M. GaunlettCo. Inc, a corporation of Washington, both of Seattle, Wash.

Filed Nov. 4, 1957, Ser. No. 694,202

2 Claims. (Cl. 74471) This invention appertains to valves forcontrolling the supply of fluid under pressure to hydraulically operatedapparatus, and relates more particularly to devices for operating aplurality of such valves either individually or simultaneously.

An object of the invention is to provide an improved hydraulic controlapparatus.

Another object is to provide an improved hydraulic valve operatingmechanism.

Another object i to provide a control mechanism whereby a plurality ofhydraulic valves can be operated either individually or simultaneouslyby a single control lever.

Another object of the invention is to provide a valve operatingmechanism having a single control lever so connected to each of twohydraulic valves that either valve can be operated through its entirerange of movement or any desired fractional part thereof withoutnecessarily altering the adjustment of the other valve regardless of thesetting of said other valve.

Another object is to provide a valve operator whereby a single controllever can be manipulated to adjust or regulate two valves eitherindividually or simultaneously to cause each valve to be adjustedoptionally in either of two directions and to any desired degree withinthe limits of its adjustability.

Another object of the present invention is to provide a controlmechanism whereby a single actuator member, such as a pivotally mountedlever, is operable to regulate two valves of the rotary type eithersimultaneously or individually.

Another object is to provide a dual valve control mechanism of thecharacter indicated which is particularly adapted for, but is notnecessarily limited to, the operation of equipment driven by twoindependent hydraulic motors, such as a derrick boom or the universallypivotable nozzle of a hydraulic monitor, and adapted to be elevated orlowered by one reversible hydraulic ram and to be swung horizontally ineither direction by another, independently operable, reversiblehydraulic ram.

These and other objects and advantages of the present invention willbecome apparent from the following description and the accompanyingdrawings, in which:

Fig. 1 is a perspective, partially broken away, of the hydraulic controlapparatus of the present invention.

Fig. 2 is a plan, partly broken away, of the control apparatus of Fig.1.

Fi 3 is a section along lines 33 of Fig. 2.

Figs. 4-7, inclusive, are plan views drawn to a reduced scale andshowing the hydraulic control apparatus of the invention in variousdifferently adjusted positions.

As illustrated in Figs. 1, 2 and 3, the hydraulic control apparatus ofthe present invention is mounted upon a base plate 12 rigidly secured asby welding to the upper end of a suitable pedestal 14. The base plate 12is in the form of a flat metal plate of suitable rigidity and preferablyis square. It is to be understood, however, that, depending upon thecircumstances of installation, the base plate 12 may be mounted directlyupon the hydraulically driven machine that the apparatus 10 of theinvention is adapted to control.

Two rotary valves 16 and 16a are fixedly mounted upon the base plate 12with their major axes perpendicular to each other. Preferably, thevalves 16 and 16a are arranged with their respective major axes parallelto and spaced but a short distance from two adjacent edges 18 and 18a ofthe base plate 12 that meet in a corner 20 of the plate 12. Each valve16 and 16a is mounted on the base plate 12 by means of an angle bracket24, the vertical flange 26 of which is secured to a stationary part ofthe associated valve by stud and nut assemblies 28 (Fig. 1) while thehorizontal fiange30 of each bracket is secured to the base plate 12 bybolt and nut assemblies 32.

Whereas the requirements of the present invention impose no restrictionsas far as the particular variety of rotary valve to be employed thereinis concerned, the valves 16 and 16a illustrated are of the typedisclosed in my copending application Serial No. 694,245, filed November4, 1957 for Hydraulic Valve, to which application reference may be hadfor a full disclosure of the construction and manner of operation of thevalves 16 and 16a. Inasmuch as the two valves 16 and 16a are ofidentical construction, the following brief description of but one ofthese valves, referring only to those features thereof that areessential to an understanding of the prescut invention, will sutfice forthe disclosure.

The valve 16 includes a body portion 22, this being the stationary partof the valve to which the associated angle bracket 24 is secured. Acylindrical valve core housing 34 is mounted on the body portion 22 withits axis coinciding with the major axis of the valve 16, for rotationaladjustment about said axes with respect to the body portion 22.Hydraulic fluid under pressure is supplied to both valves 16 and 16a byan inlet manifold 36 to which hydraulic fluid under pressure is suppliedby a suitable conduit 37. Since it is usually convenient to extend thesupply conduit 37 upward through the base plate 12, an aperture 38 isprovided in the base plate to accommodate the supply conduit and thecoupling member 40 (Fig. 2) for connecting the supply conduit to themanifold 36 which is provided on the underside of the manifold 36 inregistry with the aperture 38. The ends of the manifold 36 are providedwith flanges 42 and 42a which are bolted to the body portions 22 of thevalves 16 and 16a, respectively. Consequently, the common inlet manifold36 serves as the source of fluid under pressure for both valves 16 and16a.

The valve 16 has two ports 46 (only one of which is shown, Fig. l) inopposite sides of the body portion 22, which are internally threaded toreceive fluid lines 48 and 50, respectively (Fig. 2). These fluid lines48 and 50 hereinafter will be called the Working lines inasmuch as theyconnect the control valve 16 to opposite purposes of the present ends ofa reversible hydraulic engine (not shown) intended to be controlled bymeans of the valve 16. The body portion 22 of the valve also is providedwith a downwardly opening port (not shown) threaded to receive a fluidline 52 (Fig. 3) which hereinafter will be called the exhaust line sinceit is adapted to convey exhaust fluid from the valve 16 back to a supplyreservoir (not shown) or other suitable point of discharge.

As explained in the hereinbefore mentioned copending application, theinternal structure of the valve 16 is such that when the valve corehousing 34 is in its neutral or intermediate position as illustrated inFigs. 1-3 the valve is closed. When the valve core housing '34 isrotated as far as possible in a counter clockwise direction as viewed inFig. 1, fluid will be permitted to flow from the manifold 36, throughthe valve 16, and through the discharge port 46 whence the valvepressurized fluid can flow through the working line 48 to one end of thefluid engine (not shown) that the valve 16 is intended to control. Atthe same time that connection is established between the manifold 36 andthe working line 48, fluid conducting connection is likewise establishedwithin the valve 16 between the working port to which the. workingline50 is connected. and the discharge port to which the exhaust line--52vis connected. Thus, fluid escapingfrom the other cndof the hydraulicmotor will returnto the valve through theworking line 58 and bereturnedto the supply reservoir through the exhaust line 52. Thus, whenthe valve corehousing 34 of the valve 16 is turned counterclockwise asviewed in Fig. 1 the hydraulic motor with which the valve 16 isassociated is caused to. operate irra certain direction. When thevalvecore housing 34 is turned as far as possible in the oppositedirection the manifold 36 is connected to the working line 50 while theworking line 48 is connected to the exhaust line 52 so that theassociated hydraulic engine is caused to operate in the oppositedirection.

It will be appreciated, therefore, that since the present inventionprovides means for operating two hydraulic valve 16 and 1612, thecontrol apparatus of the invention is adapted for use in controllingoperation of various types of machinery wherein an element such as aderrick boomis moved either up or down by a double acting or reversiblehydraulic ram, which ram can be controlled by one reversing valve whilethe-same boom is caused to move horizontally in either direction byanother reversible hydraulic ram controlled by another reversing valve.

A cylindrical head or boss 60 (Figs. 1, 2 and 3) is rigidly attached tothe outer end of the valve core housing 34 of the valve 16 by means ofheaded screws 62 extending through a flange 64 on the inner end of theboss and tightened into tapped holes (not shown) provided for thepurpose in the outer end of the valve core housing. A radial slot 66 isformed inthe outer end portion of the head 60, in such position that theslot is open both at the outer end of the boss and along one sidethereof. The head 60 carries an arm or lever 68', the upper end of thearm being loosely fitted into the slot 66 and pivotally connected to thehead by a pin 70 (Pig. 3) rigid with the head and extendingdiametrically thereof across the slot 66 and through the upper end ofthe arm. The arm 68 of each valve 16 and 16a hangs vertically, downwardfrom its pivot pin 7% when the associated valveicore housing 34 is inits neutral or closed position, i.e., that position in which theassociated valve 16 or 16a prevents'flow from the inlet manifold 36.

Whereas the upper part of each arm 68 is disposed within the associatedslot 66 the lower part ofthe arm projects radially downward from thelower side ofthe associated head 60, thus providing a lever by which thehead and the valve core housing to which it.is attached can be turned byswinging the lower end of the arm either clockwise or counterclockwiseabout the axis of rotation of the associated valve core housing. It isparticularly to be observed however, that in view of the manner in whichthe upper end of the arm is pivotally connected to the associated head69, i'.e., by means of the diametrically extending pivot pin 70, eacharm 68 is free to swing toward and away from the associated valve corehousing 34 without any accompanying rotary motion of the same.

As hereinabove explained, the two valves 16 and 16a are mounted in fixedposition upon the base plate 12 with the axis of rotation of theirrespective valve core housings 34 perpendicular to each other.Consequently, the planes in which the two valve operating arms or levers68 are free to swing are perpendicular to each other, as are like wisethe respective directions in which the two arms 68 swing when effectingrotary motion of their respectively associated valve core housings 34.More specifically stated, the plane in which the valve actuating arm68of the valve 1.6 is free to swing, is parallel to the proximate edge 18of the base plate 12 and the direction in which this arm 68 moves whenimparting rotary motion to its associated valve core housing 34 isperpendicular to the edge 13 of the base plate 12.. Similarly, the planein which the actuating arm 63 of the valve 16a is free to swing withoutimparting any motion to the associated valve core housing 34 is parallelto the proximate edge 18a of the base plate 32 while the direction inwhich this arm 68 moves when imparting rotary motion to the associatedvalve core housing 34 is perpendicular to the edge 18a.

An auxiliary platform '76 is supported in a position projecting out frombelow the corner 78 of the base plate 12 opposite the hereinbe-forementioned corner 20 at which the two edges 18 and 118a of the base platemeet. The platform '76 is rigidly supported, preferably in a planeparallel to and spaced below that of the base plate 12, by a downwardlyand outwardly inclined bracket 89 (Figs. l, 2 and 3). The platform 76supports on its upper surface a socket member 82 (Figs. 1 and 3) withinwhich a ball 84 is fitted in a manner permitting the ball to turn freelyin any direction. The ball 84 is affixed to the lower end of anoperating lever 86 (Figs. 1, 2 and 3) that projects upward from thesocket member 82 and preferably carries at its upper end a knob S8 (Fig.3) that provides a convenient handle comfortably grasped by the hand ofan operator. The ball 84 at the lower end of the lever 86 is retainedwithin the socket member 82 by means or" a collar 9%} (Figs. 1 and 3),the collar 9% being retained in position by screws $2 that extend notonly through the collar 96 but likewise through the socket member 8?.and auxiliary platform '76 to anchor the socket member and the collar inoperative position. The central aperture 94 of the collar 90 is of adiameter slightly smaller than the diameter of the ball 84 and the edgeof the aperture 94 is contoured to the curvature of the ball so that thecollar 90 prevents displacement of the ball from ti 6. socket member 82while permitting unrestricted universal pi-votalmovement of the lever 86about a point at the center of the ball 84.

A second ball joint ltlil (Figs. 1, 2 and 3) is provided intermediatethe ends of the lever 86, whereby an L-shaped link member 192 isconnected to the lever 86 for universal movement thereby substantiallyin a horizontal plane. The ball and socket joint ltli) is situated atthe juncture of the two legs 1% and 104a of the L-shaped linkmember 132.Similar ball and socket joints 106 and H366; are provided at the outerends of the two legs 184 and 104a, respectively. Each of the ball andsocket joints liltl, 1% and 196a comprises upper and lower annularcollars 168 and 119, respectively, secured to the upper and lowersurfaces of the link member 1&2 by screws 112. The central openings ofthe two collars 1&8 and 110 of each ball and socket joint 10-8, 166 and1416c: are disposed in axial alignment with a circular opening 118 inthe link member 192, and since the openings of the collars 198 and 11%are slightly smaller in diameter than the associated openings 118 of thelink member the collars of each ball and socket joint 100, 106 and 106aare adapted to prevent displacement of a ball 12.6 from the associatedopening 118 of the link member. In the case of the ball and socket jointtilt) the ball 120 is carried by and is rigidly secured to the controllever 86, whereas in the cases of the ball and socket joints 166 and186a the balls 129 are rigidly secured to the lower ends of theactuating arms 63 of the valves 16 and 16a, respectively- It will beapparent, therefore, that if an operator swings the operating lever 86in the vertical plane that in eludes-the axis of thepin '70 whereby theactuating arm 68 0f the valve 16 is pivotally connected to the head 65)thereof, this head 60 and the associated valve core housing 34 -will becaused to turn about its axis, thus operating the valve 16. However,this motion of the lever 86, i;e., either toward or away from the valve16 will have no efliect upon the companion valve 16a because theaccompanying motion of the socket 106a whereby the actuating arm 68 ofthe valve 16a is connected to the link member 102 is in a directionparallel to the axis of rotation of the valve core housing 34 of thevalve 16a with the result that the only effect upon the valve 16a ofmotion of the control lever 86 toward or away from the valve 16 is topivot the actuating arm 68 thereof about the axis of its associated pin70 without imparting any rotary motion to the associated valve corehousing 34. Conversely, motion of the control lever 86 toward or awayfrom the valve 16a will cause the valve core housing 34 of the valve 16ato turn in a manner eflecting operation of the valve 16a but will haveno eflect upon the valve 16 other than to cause the actuating arm 68 ofthe valve 16 to swing on its pivot pin 70 without imparting any rotarymotion to the valve core housing 34 of the valve 16. By swinging thecontrol lever 86 in the plane that bisects the angle between the axes ofthe valves 16 and 160, both valves will be operated equally. However, ifthe operating lever 86 is swung in a plane more nearly perpendicular tothe axis of one valve and, consequently, more nearly parallel to theaxis of the other valve, both valves 16 and 1611 will be operatedsimultaneously but the valve to which the plane of movement of the leveris more nearly perpendicular will be operated to a greater extent thanthe valve to which the plane of movement of the lever is more nearlyparallel.

A specific example of an apparatus with which the control mechanism ofthe present invention can advantageously be associated is the hydraulicmining giant or monitor (not shown) of the type disclosed in theMiscovich patent, No. 2,680,650, which includes a nozzle adapted toeject a high evlocity jet of water and mounted for universal pivotalmovement. As explained in detail in the patent, two reversible hydraulicrams are associated with the giant, one in such a way that opera tion ofone ram by supplying motivating fluid to one end of the ram elevates thenozzle and supplying fluid under pressure to the other end of the sameram reverses the ram and lowers the nozzle. The other hydraulic ram isso associated with the giant that operation of the second ram in onedirection by connecting one end thereof to a source of fluid underpressure turns the giant horizontally in one direction and connectingthe other end of the second ram to the fluid pressure source reversesthe ram and causes the giant to turn horizontally in the otherdirection. Whereas the rams disclosed in the above identified patent arecontrolled automatically, the present invention provides means formanually operating such rams.

For the sake of convenience in the following description of the mannerin which the apparatus of the present invention operates the controldevice 10 will be assumed to be operatively associated with thehydraulic mining giant (not shown) of the type indicated, with each ofthe working lines 48 and 50 of the valve 16 in fluidconveyingcommunication with one of the opposite ends of the ram (not shown) thatmoves the nozzle vertically. The connections should be made in such away that when fluid under pressure is admitted to the line 50 of thevalve 16, i.e., by movement of the lever 86 away from the valve 16, theram will effect raising of the nozzle, and when motivating fluid isadmitted to the line 48 of the valve 16, i.e., by movement of the lever86 toward the valve 16, the nozzle will be lowered. The valve 160 shouldbe connected with the ram (not shown) that moves the nozzle of the gianthorizontally, and in such a way that when the lever is moved toward thevalve 16a, causing fluid to be admitted to the line 50 of the valve 16athe nozzle will turn counterclockwise as viewedfrom above, and whenfluid is admitted to the line 48 of the valve 161: by moving the leveraway from the valve 160, the nozzle will turn clockwise.

Figs. 1, 2 and 3 show the control apparatus 10 of the invention in itsneutral position, i.e., with both valves 16 and 16a closed, with theresult that both lines 48 and 50 of both valves 16 and 16a are bankedoff. Therefore, the nozzle of the giant remains stationary when theapparatus 10 is in this arrangement, in which the operat= ing handle 86'is vertical, as are also the valve actuating arms 68 of both valves 16and 16a.

The operator should take a position behind the control apparatus 10 anddirectly in line with the leg 164 of the link member 102. The leg 164aof the link member 102 will then project to the left of the operator.This makes it possible for him to aim the nozzle of the hydraulic giantin any desired direction within its range of movement by moving theoperating handle 86 in the manner that is most natural, i.e., the mannerthat most closely simulates the desired movement of the nozzle. Forexample, if the jet stream from the giant is being directed against avertical cliff or bank, and it is desired to swing the nozzle of thegiant rapidly upward so that the jet stream impinges against a higherarea of the bank, the operator should pull the lever 86 all the wayback, i.e., straight toward himself, causing the apparatus 7 to occupysubstantially the position illustrated in Fig. 4. This will cause thevalve core housing 34 of the valve 16 to turn clockwise as viewed inFig. l, to the limit of its movement in that direction. This establishesconnec tion between the inlet manifold 36 and the working fluid line 50of the valve 16 so that hydraulic fluid is admitted under full flow tothe ram that turns the nozzle vertically and in such a way that thenozzle is elevated as rapidly as possible. If upward movement of thenozzle at a slower speed is desired, the handle 86 should be pulledback, toward the operator, but not as far as when maximum speed isdesired. This will permit flow from the manifold 36 to the line 56 ofthe valve 16, but at a restricted rate, so that the ram will be operatedin the same direction, but more slowly.

When it is desired to lower the nozzle of the giant so as to direct itsjet stream against a lower area, the operator should push the controllever 86 forward, i.e., away from himself; and if maximum speed inattaining the new adjustment of the giant is desired the lever 86 shouldbe moved as far forward as'possible. The apparatus 14 will then occupysubstantially the position illustrated in Fig.5 wherein the actuatingarm 68 of the valve 16 slopes downward and forward and the valve corehousing 34 associated therewith will be turned as far as possible in acounterclockwise direction as viewed in Fig. 1. This will establish fullcommunication between the inlet manitold 36 and the working fluid line48 of the valve 16 causing fluid to flow at maximum rate to the ram thatmoves the nozzle vertically and in a manner causing the nozzle to swingdownward. As in the previously-described instance, if a more moderaterate of movement of the nozzle is desired the operating handle 86 shouldnot be moved so far forward.

It is to be observed that in both the Fig. 4 and Fig. 5 positions, ineach of which the operating handle 86 has been moved only in a verticalplane substantially perpendicular to the axis of the valve 16, theactuating arm 68 of the valve 16a has likewise moved only in a verticalplane parallel to or including the axes of the valve 16a. Under thesecircumstances, the valve core housing 34 of the valve 16a remainsmotionless with the result that the valve 16a remains in its neutralposition and both of its working lines a8 and 50 remain blanked off andthe ram associated therewith, i.e., the ram that effects horizontalmovement of the nozzle, likewise remains motionless.

Assuming now that while the nozzle of the giant is being moved downwardas the result of shifting the operating handle 86 to the Fig. 5position, it is desired to have the nozzle of the giant swing clockwiseas viewed in Fig. 5, i.e., to the operators right. The handle 86 can beswung to the right and if maximum speed of movement of the nozzle isdesired the handle should be moved as far as possible to the right. Thiswill cause the parts of the apparatus 10 to assume substantially theposition illustrated in Fig. 6 wherein the actuating arm 68 of the valve16:: is swung to the right, turning the valve core housing 34 of thevalve 16a counterclockwise as viewed in Fig. 1 and thus establishingfull flow 'of hydraulic fluid from the manifold 36 to the working line48 of the valve 16a which, as stated hereinabove, is connected to theram that effects horizontal movement of the nozzle of the giant and insuch a way that the nozzle is caused to swing to the operators right.

Since the ball 120 at the lower end of the actuating arm 68 of the valve16 connects this arm 63 and the link 102 in a manner permittinguniversal relative movement between these two members, the leg 104 ofthe link mem- 1 her 102 may merely pivot about a vertical axis as thelink member 1432 moves from the Fig. 5 position to the Fig. 6 position,thus permitting the arm 68 of the valve 16 to remain motionless. Undersome circumstances,

however, the link member 102 will move from the Fig.

5 position to the Fig. 6 position in translatory motion, wherein the leg164 remains parallel to its Fig. 5 position as it moves laterally. Asthis occurs, the arm 68 of the valve 16 will swing outward about theaxis of its pivot pin 76 so that it will then slope outward anddownward, projecting beyond the vertical plane of the end of theassociated head 66 in a position corresponding to that of the arm 68 ofthe valve 16a illustrated in Fig. 4. Whether movement of the operatinghandle 86 from the Fig. 5 position to the Fig. 6 position is accompaniedby pivotal movement of the leg 104 about the ball 120 of the valve 16,leaving the associated arm 68 stationary, or whether such movement ofthe operating lever 86 causes the arm 63 of the valve 16 to swingoutward, or whether a combination of both movements occurs, depends uponthe relative amount of friction between the. several relatively movableparts of the apparatus. The result, however, is the same because inany-case the valve core housing 34 of the valve 16 remains motionless,and the setting of the valve 16 is not changed as the valve 16a isadjusted as the result of lateral movement of the handle 86.

As a further example of the manner in which the apparatus 10 can beoperated to control the hydraulic giant, let it he assumed that it isdesired to have the nozzle of the giant swing upward and to theoperators left. This is accomplished by swinging the handle toward theoperator and to his left and if maximum speed of movement of the nozzleis desired the handle 86 should be moved as far as possible. The partsof the apparatus will then occupy the positions illustrated in Fig. 7wherein both valves 16 and 16a have been actuated to admit fluid underpressure to the working line 59 of the valve 16 and to the working line50 of the valve 16a. Consequently,

both rams of the hydraulic giant will be operated simultaneously causingthe nozzle to swing upward and to the left. The nozzle will continue tomove thus until the handle 86 is moved to another position. If thehandle is returned to its upright position, the nozzle will beimmobilized in the position which it has then attained.

It is to be realized that the control lever 86 can be swung from anyposition to any other desired position without having to be returned toits neutral'or upright position and that the actuating arms 68 of thetwo valves 16 and 16a will be moved accordingly by the link member 162so as to adjust the valves 16 and 16a in accordance with the attainedposition or" the control lever 86. Moreover, the two valves 16 and 16acan easily and quickly be adjusted to any desired setting eitherindividually or simultaneously and in either direction at the willof theoperator. The extent of movement of each valve is proportional totheextent of movement of the' operating lever 86 toward or away fromthat valve and any movement of the operating lever-86 toward or awayfrom eithervalve has noeffect upon the setting of the in a plane that isoblique to the axes of 'both valves, the" companionvalve, and in theevent that the lever is swung valve whose axis is more nearlyperpendicular to the plane of movement of the lever will-be. adjusted tothegreater extent. Therefore, the operator has at his command aninfinite number of settings of the operating lever 86 so that theapparatus 14) is effective to cause movement of the nozzle of thehydraulic giant in any desired direction within the limits of itsadjustment and at any desired speed within the limits determined by themaximum velocity of flow of fluid through the various hydraulic lines.

In this same connection, it is to be observed that when the two valves16 and 16a are operatively connected to the respective rams of thehydaulic giant in the manner explained hereinabove, the apparatus 10 ofthe invention enables the operator to control the hydraulic giantaccurately and with the greatest case, since the nozzle responds tomovement of the control lever 86 practically immediately. Furthermore,in order to effect movement of the nozzle in a desired direction and ata desired speed, the manner in which the control lever 86 must bemanipu-- lated is precisely that which seems most natural to attainthedesired result. This feature of the present invention makes the manualcontrol of the hydraulic giant almost automatic with the operator, sinceonly a minimum of mental effort is required therefor.

Although the apparatus 10 of the present invention has been describedhereinabove as being eifective to control movement of a derrick boom orthe nozzle of a hydraulic giant, it is to be understood that thesedevices have been referred to hereinabove merely in an exemplary, andnot in a limiting, sense, because the apparatus 10 is equally efiectivewhen used to control movement of other structures in two directionseither simultaneously or otherwise by means of two independentlyoperable hydraulic engines. Furthermore, while a particular embodimentof the present invention has been shown and described, it will beunderstood that the apparatus is capable of moditication and variationwithout departing from the prin ciples of the invention and that thescope of the invention should be limited only by the scope and properinterpretation of the claims appended hereto.

The invention having thus been described, what is believed to be new anddesired to be protected by Letters Patent is:

1. In a control apparatus for a pair of rotary valves each including amember rotatable to effect operation of the valve, and with the axes ofthe members perpendicular to each other in a plane including both ofsaid axes, an actuating arm projecting radially from each of said rotarymembers and mounted thereon for movement therewith about said axis ofrotation of the associated rotary member and for pivotal movementrelative thereto in a plane including said axis of the asso ciatedrotary member, an actuating lever mounted for universal pivotalmovement, a link structure, means pivotally connecting said linkstructure to said lever for universal substantially planar movement bythe iever, and means pivotally connecting each or" said actuating armsto the link structure for pivotal movement thereby. 2. Control apparatuscomprising two rotary control members, said control members beingpositioned with their axes of rotation perpendicular to each other in aplane including both of said axes, an actuating arm projecting radiallyfrom cachet said rotary members and mounted thereon for movementtherewith about the axis of rotation of the associated rotary member andfor pivotal movement relative thereto in a plane including said axis ofthe associated rotary member, an actuating lever mounted for universalpivotal movement, a rigid link structure, means pivotall'y connectingsaid link; structure to said lever for universal substantially pianarmovement by the lever, and mcanspivotally connecting 9 10 each of saidactuating arms to the link structure for piv- 2,551,442 yKuhlman May 1,1951 otal movement thereby. 2,613,548 Davis Oct. 14, 1952 2,700,904Woods Feb. 1, 1955 References Cited in the file of this patent 2,753,145'Rosebrook July 3, 1956 UNITED STATES PATENTS 5 FOREIGN PATENTS1,176,784 Speiden Mar. 28, 1916 541,988 Great Britain Dec. 22, 19412,337,166 Overbeke Dec. 21, 1943

